EP2207982B1 - Frein de véhicule combiné avec frein de stationnement à actionnement électromécanique - Google Patents

Frein de véhicule combiné avec frein de stationnement à actionnement électromécanique Download PDF

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Publication number
EP2207982B1
EP2207982B1 EP08843095A EP08843095A EP2207982B1 EP 2207982 B1 EP2207982 B1 EP 2207982B1 EP 08843095 A EP08843095 A EP 08843095A EP 08843095 A EP08843095 A EP 08843095A EP 2207982 B1 EP2207982 B1 EP 2207982B1
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EP
European Patent Office
Prior art keywords
brake
gear
rolling bodies
piston
combined vehicle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP08843095A
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German (de)
English (en)
Other versions
EP2207982A1 (fr
Inventor
Thomas Winkler
Willi Zeig
Thomas Hess
Marcus Schumann
Anja Klimt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Publication of EP2207982A1 publication Critical patent/EP2207982A1/fr
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Publication of EP2207982B1 publication Critical patent/EP2207982B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/22—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members
    • F16H25/2204—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls
    • F16H25/2233—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls with cages or means to hold the balls in position
    • F16H25/2238—Screw mechanisms with balls, rollers, or similar members between the co-operating parts; Elements essential to the use of such members with balls with cages or means to hold the balls in position using ball spacers, i.e. spacers separating the balls, e.g. by forming a chain supporting the balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2123/00—Multiple operation forces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/52—Rotating members in mutual engagement with non-parallel stationary axes, e.g. worm or bevel gears

Definitions

  • the present invention relates to a combined vehicle brake having a hydraulically actuated service brake and an electromechanically actuated parking brake device, wherein in a brake housing, a hydraulic operating pressure chamber is limited by a brake piston, which is acted upon for performing service braking with hydraulic pressure medium, so that the brake piston to achieve a braking action along a piston longitudinal axis is operable, and wherein the parking brake device acts on the brake piston by means of a gear by the transmission translates the rotational movement of an electromechanical actuator in a translational movement and causes actuation of the brake piston for performing parking brake operations and holds in the actuated position, wherein the gear has a threaded spindle and a threaded nut, which are in contact with each other via a plurality of rolling elements.
  • Such a hydraulic vehicle brake with electrically operated parking brake device is, for example from the DE 101 50 803 B4 known.
  • a transmission is provided, which converts the rotational movement of the electric motor into a longitudinal movement of the brake piston to achieve a locking force according to the operating principle of a threaded nut spindle arrangement.
  • this gear unit is designed as a so-called “spindle / ball bearing bushing arrangement", which is also called ball screw or ball screw.
  • These ball screws have a threaded spindle and a threaded nut, which are in contact with each other via a plurality of rolling elements.
  • the rolling elements are movably limited between two stops in the thread, wherein a spring element between the rolling elements and a stop is arranged and allows for a load-free operation of the transmission slipping of the rolling elements, and upon actuation of the transmission under load Rolling the rolling elements causes and wherein between the rolling elements at least one further spring element is provided as an intermediate spring element, the friction force between the rolling elements with each other Actuator of the gear reduced.
  • the intermediate springs keep a path, as the outside in the load-free case by the spring preload sitting balls must roll when pressed under load on a smaller diameter.
  • the ratio of the number of rolling elements to the number of intermediate spring elements is constant, so that with a larger number of rolling elements, a larger number of intermediate spring elements is used.
  • the intermediate spring elements are distributed uniformly between the rolling elements.
  • the intermediate spring elements are designed as helical compression springs or as elastomer springs.
  • the attacks are non-positively connected to the threaded nut or formed integrally with the threaded nut.
  • a further advantageous embodiment provides that the first stop has a support surface for the spring element, while the other stop a stop surface for the second spring element, which acts as a pre-compression spring element has.
  • hydraulic vehicle brake has on the one hand a hydraulically actuated service brake and on the other hand, an electromechanically actuated parking brake.
  • the vehicle brake is performed in the example shown as a floating caliper disc brake whose caused by a hydraulic actuation function is well known to those skilled in this field and therefore need not be explained in more detail.
  • the actuation of the parking brake is an electromechanical actuator 7 or electric motor 7, which is integrated in a drive module 21 together with a two-stage transmission, the required sensors and an electronic control unit 22.
  • the above-mentioned vehicle brake further comprises a brake housing or a caliper 2.0. on, which surrounds the outer edge of a brake disc, not shown, and two arranged on both sides of the brake disc brake pads 26, 27.
  • the brake housing 20 forms on its inside a brake cylinder 9, a brake piston 5 axially slidably receives.
  • Brake fluid can be supplied to the operating pressure chamber 6 formed between the brake cylinder 9 and the brake piston 5 for performing service braking, so that a brake pressure is built up which displaces the brake piston 5 axially along a piston longitudinal axis A towards the brake disk.
  • the brake pad 27 facing the brake piston 27 is pressed against the brake disk, wherein in response the brake housing 20 shifts in the opposite direction and thereby also presses the other brake pad 26 against the brake disk.
  • a parking brake device for carrying out parking brake operations is electromechanically operable and also acts on the brake piston 5.
  • a transmission 1 is provided which converts the rotational movement of the electromechanical actuator 7 or electric motor 7 into a translational movement and an actuation of the brake piston 5 along the axis A causes.
  • the transmission 1 is essentially formed by a threaded spindle 2 and a threaded nut 3, which are connected to one another via rolling elements 4.
  • the rolling elements 4 are formed as balls.
  • a connected to the threaded spindle 2 shaft 17 protrudes on the side facing away from the brake disc from the brake housing 20 and is driven by the above-mentioned electromechanical actuator 7 with the interposition of a two-step reduction gear.
  • means for sealing the operating pressure chamber 6 in the bore of the brake housing 20, through which the shaft 17 projects, are provided.
  • the transmitted to the threaded spindle 2 rotational movement is transmitted via the balls 4, which are in the thread between the threaded spindle 2 and the nut 3, on the threaded nut 3, the translational movement in the direction of the axis A completes.
  • the brake piston 5 is actuated, on which the threaded nut 3 is supported.
  • the threaded spindle 2 is received by a stepped bore 30 in the brake housing 20 and is supported via a connected to the spindle 2 collar 19 and a thrust bearing 18 on the brake housing 20 from.
  • the transmission 1 thus converts the rotational movement of the electromechanical actuator 7 into a linear movement and is responsible for the generation of the application force for carrying out a parking brake operation.
  • the electric motor 7 When releasing the parking brake device, the electric motor 7 is operated in accordance with the opposite direction and the threaded nut 3 and thus also the brake piston 5 perform a movement in the drawing to the right.
  • the brake pads 26, 27 are no longer in contact with the brake disc and the parking brake operation is completed.
  • the two-stage transmission is designed as a worm gear 11, 12.
  • Worm gearboxes are a category of helical gearboxes in which, in contrast to the Wälzgetrieben also a sliding portion in the movement is present.
  • Such a worm gear is constructed from a helically toothed wheel, a worm, and a helical gear meshing therewith, the worm wheel.
  • the first gear stage that is to say the first worm gear 11, is connected on the input side to the output shaft 8 of the electric motor 7, while the second gear stage, that is to say the second worm gear 12, on the output side is connected to the shaft 17 and the transmission 1 and 2, 3.
  • a first worm 13 is fitted onto the output shaft 8 of the electric motor 7 and meshes with a first worm gear 14.
  • a second worm 15 is mounted on the center of rotation of the first worm gear 14 and is rotated by it.
  • the second worm 15 in turn meshes with a second worm wheel 16, which is rotatably connected to the shaft 17 and the shaft 17 is rotated together with the gear 1 in rotation while a translational movement of the brake piston 5 is generated. So that the set in this way application force is maintained during a parking brake operation, the second worm gear 12 is designed self-locking.
  • the rolling elements 4 Upon actuation of the transmission 1 under load, the rolling elements 4 roll in the thread. As a result, a relatively high efficiency of 85% to 95% is achieved, or taking into account the friction losses on the thrust bearing 18 75% to 85%.
  • the rolling elements 4 slip, ie until the brake piston 5 associated brake pad 34 bears against the brake disc, not shown, slip the balls 4, because this is a virtually no-load operation. Only under load, the balls 4 start to roll or unroll.
  • the transmission 1 thus acts simultaneously as adjustment if the brake pads 26, 27 are worn.
  • the absence of a separate adjusting device or the integration of adjusting and actuating device in a single component is particularly inexpensive and at the same time robust.
  • a spring element 10 is provided which maintains a rolling path for rolling the rolling elements 4.
  • the rolling elements 4 are pressed against each other and rub against each other when rolling.
  • the friction between the rolling elements 4 with each other deteriorates the efficiency of the transmission 1, so that more intermediate spring elements 25 are arranged between the rolling elements 4, which reduce the contact pressure between the rolling elements 4 and thus reduces the frictional force between the rolling elements 4.
  • the number and position of the intermediate spring elements 25 can be varied in order to effectively reduce the friction between the rolling elements 4.
  • the intermediate spring elements 25 are evenly distributed between the rolling elements 4, ie after a predetermined number of rolling elements 4, the next intermediate spring element 25 is arranged. By this measure, a uniform reduction of the frictional force between the rolling elements (4) is realized with each other.
  • the intermediate spring elements are, as in Fig. 2 represented, formed by helical compression springs. But it is also possible, for example elastomeric springs.
  • the rolling elements 4 are arranged movably between two stops 23, 24 in the thread limited, wherein the aforementioned spring element 10 is arranged to provide a Wälzweges for the rolling elements 4 between the rolling elements and the first stop 23.
  • the first stop 23 therefore has a bearing surface for the spring element 10.
  • a second, not shown spring element is between the rolling elements 4 and the other stop 24 and serves as a so-called form spring.
  • This pre-compression spring is supported on the second stop 24, which has a stop surface for the pre-compression spring element, not shown.
  • Both stops 23, 24 are non-positively connected to the threaded nut 3 or formed integrally with the threaded nut 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Braking Elements And Transmission Devices (AREA)

Claims (7)

  1. Frein de véhicule combiné, qui présente un frein de service à actionnement hydraulique et un frein de stationnement à actionnement électromécanique, dans lequel une chambre hydraulique de pression de service (6) est limitée dans un boîtier de frein (20) par un piston de frein (5), qui peut être soumis à un fluide comprimé hydraulique pour l'exécution de freinages de service, de telle manière que le piston de frein (5) puisse être actionné le long d'un axe longitudinal de piston (A) pour obtenir un effet de freinage, et dans lequel le dispositif de frein de stationnement agit sur le piston de frein (5) au moyen d'une transmission (1), en ce que la transmission (1) convertit le mouvement de rotation d'un actionneur électromécanique (7) en un mouvement de translation et provoque un actionnement du piston de frein (5) pour l'exécution d'opérations du frein de stationnement et le maintient dans la position actionnée, dans lequel la transmission (1) comprend une broche filetée (2) et un écrou fileté (3), qui sont en contact l'un avec l'autre au moyen de plusieurs corps de roulement (4), caractérisé en ce que les corps de roulement (4) sont disposés de façon mobile limitée entre deux butées (23, 24) dans le filet, dans lequel un élément de ressort (10) est disposé entre les corps de roulement (4) et une butée (23) et permet un glissement des corps de roulement (4) lors d'un actionnement sans charge de la transmission (1) et provoque un roulement des corps de roulement (4) lors d'un actionnement de la transmission (1) sous charge, et dans lequel il est prévu comme élément de ressort intermédiaire (25) entre les corps de roulement (4), au moins un autre élément de ressort qui réduit la force de frottement entre les corps de roulement (4) entre eux lors de l'actionnement de la transmission (1).
  2. Frein de véhicule combiné selon la revendication 1, caractérisé en ce qu'il est prévu un deuxième élément de ressort, qui est disposé entre les corps de roulement (4) et l'autre butée (24).
  3. Frein de véhicule combiné selon l'une quelconque des revendications 1 à 2, caractérisé en ce que les éléments de ressort intermédiaires (25) sont répartis uniformément entre les corps de roulement (4), afin de réaliser une réduction uniforme de la force de frottement entre les corps de roulement (4) entre eux.
  4. Frein de véhicule combiné selon l'une quelconque des revendications précédentes, caractérisé en ce que les éléments de ressort intermédiaires (25) se présentent sous la forme de ressorts hélicoïdaux comprimés.
  5. Frein de véhicule combiné selon l'une quelconque des revendications 1 à 3, caractérisé en ce que les éléments de ressort intermédiaires (25) se présentent sous la forme de ressorts en élastomère.
  6. Frein de véhicule combiné selon l'une quelconque des revendications précédentes, caractérisé en ce que les butées (23, 24) sont assemblées par complémentarité de force à l'écrou fileté (3) ou sont réalisées d'une seule pièce avec l'écrou fileté (3).
  7. Frein de véhicule combiné selon la revendication 6, caractérisé en ce que la première butée (23) présente une face d'appui pour l'élément de ressort (10), tandis que l'autre butée (24) présente une face de butée pour le deuxième élément de ressort.
EP08843095A 2007-10-27 2008-10-21 Frein de véhicule combiné avec frein de stationnement à actionnement électromécanique Active EP2207982B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007051455 2007-10-27
DE102008051350A DE102008051350A1 (de) 2007-10-27 2008-10-15 Kombinierte Fahrzeugbremse mit elektromechanisch betätigbarer Feststellbremse
PCT/EP2008/064209 WO2009053359A1 (fr) 2007-10-27 2008-10-21 Frein de véhicule combiné avec frein de stationnement à actionnement électromécanique

Publications (2)

Publication Number Publication Date
EP2207982A1 EP2207982A1 (fr) 2010-07-21
EP2207982B1 true EP2207982B1 (fr) 2011-03-02

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Application Number Title Priority Date Filing Date
EP08843095A Active EP2207982B1 (fr) 2007-10-27 2008-10-21 Frein de véhicule combiné avec frein de stationnement à actionnement électromécanique

Country Status (7)

Country Link
US (1) US8684147B2 (fr)
EP (1) EP2207982B1 (fr)
KR (1) KR20100090274A (fr)
CN (2) CN101836008A (fr)
AT (1) ATE500439T1 (fr)
DE (2) DE102008051350A1 (fr)
WO (1) WO2009053359A1 (fr)

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WO2022007988A1 (fr) 2020-07-10 2022-01-13 Schaeffler Technologies AG & Co. KG Vis à billes et procédé de fonctionnement d'une vis à billes
DE102021122104B3 (de) 2021-08-26 2022-09-29 Schaeffler Technologies AG & Co. KG Lageranordnung mit Freilauffunktion, Linearaktuator und Verfahren zum Betrieb eines Linearaktuators
WO2023232174A1 (fr) 2022-06-03 2023-12-07 Schaeffler Technologies AG & Co. KG Entraînement à vis à billes et actionneur électromécanique
DE102022121496A1 (de) 2022-07-29 2024-02-01 Schaeffler Technologies AG & Co. KG Wälzgewindetrieb und Verfahren zur Auslegung und zum Betrieb eines Wälzgewindetriebs

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DE102011079040A1 (de) 2011-07-12 2013-01-17 Continental Teves Ag & Co. Ohg Verfahren zum hydraulischen Unterstützen einer elektrischen Parkbremse eines Fahrzeugs
KR101924246B1 (ko) 2011-06-20 2018-11-30 콘티넨탈 테베스 아게 운트 코. 오하게 차량의 전기적 주차 브레이크를 유압식으로 부스팅하는 방법
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CN104411995A (zh) * 2012-07-05 2015-03-11 株式会社Tbk 盘式制动装置
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KR102672824B1 (ko) * 2017-02-21 2024-06-05 에이치엘만도 주식회사 전자식 디스크 브레이크
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DE102017109143A1 (de) 2017-04-28 2018-10-31 Schaeffler Technologies AG & Co. KG Rollengewindetrieb
CN109424667B (zh) * 2017-08-29 2020-11-06 比亚迪股份有限公司 盘式制动器及车辆
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FR3077051B1 (fr) * 2018-01-23 2020-01-24 Foundation Brakes France Dispositif d'ecrou forme par un manchon et un fil metallique
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JP7151354B2 (ja) * 2018-10-09 2022-10-12 株式会社ジェイテクト ボールねじ装置
DE102018217558A1 (de) * 2018-10-12 2020-04-16 Continental Automotive Gmbh Elektroantrieb, Bremsvorrichtung und Fahrzeug
US11339842B2 (en) 2019-03-26 2022-05-24 Akebono Brake Industry Co., Ltd. Brake system with torque distributing assembly
DE102019205911A1 (de) * 2019-04-25 2020-10-29 Robert Bosch Gmbh Elektromechanischer Bremsdruckerzeuger mit einer Gewindetriebanordnung und Fahrzeug umfassend einen elektromechanischen Bremsdruckerzeuger
CN112303150B (zh) * 2019-07-31 2022-04-15 比亚迪股份有限公司 线控制动系统和车辆
US11536355B2 (en) * 2019-08-28 2022-12-27 Koyo Bearings North America Llc Segmented spring for a ball screw
DE102019215836A1 (de) * 2019-10-15 2021-04-15 Continental Teves Ag & Co. Ohg Linearaktor und Bremssystem
US11585417B2 (en) * 2019-11-08 2023-02-21 Schaeffler Technologies AG & Co. KG Ball screw nut with end stop for reset spring
JP7435138B2 (ja) * 2020-03-26 2024-02-21 株式会社ジェイテクト ボールねじ装置
CN111873967B (zh) * 2020-07-31 2021-10-29 中车青岛四方车辆研究所有限公司 制动动力装置、液压制动系统及轨道列车
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DE102020118230A1 (de) 2020-07-10 2022-01-13 Schaeffler Technologies AG & Co. KG Kugelgewindetrieb und Verfahren zum Betrieb eines Kugelgewindetriebs
DE102021122104B3 (de) 2021-08-26 2022-09-29 Schaeffler Technologies AG & Co. KG Lageranordnung mit Freilauffunktion, Linearaktuator und Verfahren zum Betrieb eines Linearaktuators
WO2023025342A1 (fr) 2021-08-26 2023-03-02 Schaeffler Technologies AG & Co. KG Ensemble palier à fonction roue libre, actionneur linéaire et procédé de fonctionnement d'un actionneur linéaire
WO2023232174A1 (fr) 2022-06-03 2023-12-07 Schaeffler Technologies AG & Co. KG Entraînement à vis à billes et actionneur électromécanique
DE102022114070A1 (de) 2022-06-03 2023-12-14 Schaeffler Technologies AG & Co. KG Kugelgewindetrieb und elektromechanischer Aktuator
DE102022121496A1 (de) 2022-07-29 2024-02-01 Schaeffler Technologies AG & Co. KG Wälzgewindetrieb und Verfahren zur Auslegung und zum Betrieb eines Wälzgewindetriebs
DE102022121496B4 (de) 2022-07-29 2024-05-29 Schaeffler Technologies AG & Co. KG Gewindetrieb

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CN105333037A (zh) 2016-02-17
KR20100090274A (ko) 2010-08-13
CN101836008A (zh) 2010-09-15
ATE500439T1 (de) 2011-03-15
EP2207982A1 (fr) 2010-07-21
DE102008051350A1 (de) 2009-04-30
US8684147B2 (en) 2014-04-01
DE502008002777D1 (de) 2011-04-14
US20110162935A1 (en) 2011-07-07

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